Transmission having at least ten speeds

ABSTRACT

A transmission of the present invention has an input member, an output member, two planetary gear sets, a planetary gear set assembly, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The planetary gear set assembly includes first, second, third, fourth and fifth members. The torque transmitting devices may include clutches and brakes. The torque transmitting devices are selectively engageable in combinations of at least two to establish at least ten forward speed ratios and at least one reverse speed ratio.

FIELD

The present invention relates generally to a multiple speed transmissionhaving a plurality of planetary gear sets and a plurality of torquetransmitting devices, and more particularly to a transmission having tenor more speeds, two planetary gear sets, a planetary gear set assemblyand a plurality of torque transmitting devices.

BACKGROUND

The statements in this section merely provide background informationrelated to the present disclosure and may or may not constitute priorart.

A typical multiple speed transmission uses a combination of frictionclutches and brakes, planetary gear arrangements and fixedinterconnections to achieve a plurality of gear ratios. The number andphysical arrangement of the planetary gear sets, generally, are dictatedby packaging, cost and desired speed ratios.

While current transmissions achieve their intended purpose, the need fornew and improved transmission configurations which exhibit improvedperformance, especially from the standpoints of efficiency,responsiveness and smoothness and improved packaging, primarily reducedsize and weight, is essentially constant. Accordingly, there is a needfor an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member, aplanetary gear set assembly having a first sun gear, a second sun gear,a first ring gear, a second ring gear and a carrier member, a first andsecond planetary gear sets having a sun gear, a ring gear and a carriermember, a plurality of coupling members and a plurality of torquetransmitting devices. The torque transmitting devices are for exampleclutches and brakes.

In an aspect of the present invention, the input member is continuouslyinterconnected with the sun gear of the first planetary gear set.

In another aspect of the present invention, the output member iscontinuously interconnected with the second ring gear of the planetarygear set assembly a first interconnecting member continuouslyinterconnects the sun gear of the first planetary gear set with ringgear of the third planetary gear set.

In yet another aspect of the present invention, a first interconnectingmember continuously interconnects the ring gear of the first planetarygear set with the carrier member of the second planetary gear set andthe first sun gear of the planetary gear set assembly.

In yet another aspect of the present invention, a second interconnectingmember continuously interconnects the carrier member of the firstplanetary gear set with the ring gear member of the second planetarygear set.

In still another aspect of the present invention, a thirdinterconnecting member continuously interconnects the sun gear of thesecond planetary gear set with the second sun gear of the planetary gearset assembly.

In still another aspect of the present invention, a first torquetransmitting device is selectively engageable to interconnect the inputshaft member and the sun gear of the first planetary gear set with thecarrier member of the planetary gear set assembly.

In still another aspect of the present invention, a second torquetransmitting device is selectively engageable to interconnect thecarrier member of the first planetary gear set and the ring gear of thesecond planetary gear set with the carrier member of the planetary gearset assembly.

In still another aspect of the present invention, a third torquetransmitting device is selectively engageable to interconnect thecarrier member of the first planetary gear set with the stationarymember.

In still another aspect of the present invention, a fourth torquetransmitting device is selectively engageable to interconnect the sungear of the second planetary gear set and the second sun gear of theplanetary gear set assembly the with the stationary member.

In still another aspect of the present invention, a fifth torquetransmitting device is selectively engageable to interconnect the ringgear of the first planetary gear set, the carrier member of the secondplanetary gear set and the firs sun gear of the planetary gear setassembly with the stationary member.

In still another aspect of the present invention, a sixth torquetransmitting device is selectively engageable to interconnect the firstring gear of the planetary gear set assembly with the stationary member.

In still another aspect of the present invention, the torquetransmitting devices are each selectively engageable in combinations ofat least two to establish at least ten or eleven forward speed ratiosand at least one reverse speed ratio between the input member and theoutput member.

Further aspects and advantages of the present invention will becomeapparent by reference to the following description and appended drawingswherein like reference numbers refer to the same component, element orfeature.

DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of a ten or eleven speedtransmission according to the present invention;

FIG. 2 is a diagrammatic view of an embodiment of a ten or eleven speedtransmission according to the present invention; and

FIG. 3 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the ten speed transmissionillustrated in FIGS. 1 and 2.

FIG. 4 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the eleven speed transmissionillustrated in FIGS. 1 and 2.

DETAILED DESCRIPTION

The following description is merely exemplary in nature and is notintended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that in the particular exampleprovided, the ten or eleven speed automatic transmission of the presentinvention has an arrangement of permanent mechanical connections betweenthe components or elements of the four planetary gear sets. A firstcomponent or element of the first planetary gear set is permanentlycoupled to a second component or element of a second planetary gear setand to a third component or element of a third planetary gear set. Asecond component or element of the first planetary gear set ispermanently coupled to a third component or element of a secondplanetary gear set. A first component or element of a second planetarygear set is permanently coupled to a third component or element of afourth planetary gear set. A second component or element of a thirdplanetary gear set is permanently coupled to a second component orelement of a fourth planetary gear set.

Referring now to FIG. 1, an embodiment of a ten speed transmission 10 isillustrated in a lever diagram format. A lever diagram is a schematicrepresentation of the components of a mechanical device such as anautomatic transmission. Each individual lever represents a planetarygear set wherein the three basic mechanical components of the planetarygear set are each represented by a node. Therefore, a single levercontains three nodes: one for the sun gear, one for the planet gearcarrier, and one for the ring gear. In some cases, two levers may becombined into a single lever having more than three nodes (typicallyfour nodes). For example, if two nodes on two different levers areinterconnected through a fixed connection they may be represented as asingle node on a single lever. The relative length between the nodes ofeach lever can be used to represent the ring-to-sun ratio of eachrespective gear set. These lever ratios, in turn, are used to vary thegear ratios of the transmission in order to achieve appropriate ratiosand ratio progression. Mechanical couplings or interconnections betweenthe nodes of the various planetary gear sets are illustrated by thin,horizontal lines and torque transmitting devices such as clutches andbrakes are presented as interleaved fingers. If the device is a brake,one set of the fingers is grounded. Further explanation of the format,purpose and use of lever diagrams can be found in SAE Paper 810102, “TheLever Analogy: A New Tool in Transmission Analysis” by Benford andLeising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, a firstplanetary gear set 14, a second planetary gear set 16, a third planetarygear set 18, a fourth planetary gear set 20 and an output shaft ormember 22. In the lever diagram of FIG. 1, the first planetary gear set14 has three nodes each: a first node 14A, a second node 14B and a thirdnode 14C. The second planetary gear set 16 has three nodes each: a firstnode 16A, a second node 16B and a third node 16C. The third planetarygear set 18 has three nodes each: a first node 18A, a second node 18Band a third node 18C. The fourth planetary gear set 20 has three nodeseach: a first node 20A, a second node 20B and a third node 20C.

The first node 14A of the first planetary gear set 14 is coupled to thesecond node 16B of the second planetary gear set 16 and to third node18C of the third planetary gear set 18. The second node 14B of the firstplanetary gear set 14 is coupled to the third node 16C of the secondplanetary gear set 16. The first node 16A of the second planetary gearset 16 is coupled to third node 20C of the fourth planetary gear set 20.The second node 18B of the third planetary gear set 18 is coupled to thesecond node 20B of the fourth planetary gear set 20. The input member 12is coupled to the third node 14C of the first planetary gear set 14. Theoutput member 22 is coupled to the first node 20A of the fourthplanetary gear set 20.

A first clutch 24 selectively connects the first node 14C of the firstplanetary gear set 14 and the input member 12 with the second node 18Bof the third planetary gear set 18 and with the second node 20B of thefourth planetary gear set 20. A second clutch 26 selectively connectsthe second node 14B of the first planetary gear set 14 and the thirdnode 16C of the second planetary gear set 16 with the second node 18B ofthe third planetary gear set 18 and with the second node 20B of thefourth planetary gear set 20. A first brake 28 selectively connects thesecond node 14B of the first planetary gear set 14 and the third node16C of the second planetary gear set 16 with a stationary element or atransmission housing 50. A second brake 30 selectively connects firstnode 16A of the second planetary gear set 16 and third node 20C of thefourth planetary gear set 20 with a stationary element or a transmissionhousing 50. A third brake 32 selectively connects first node 14A of thefirst planetary gear set 14, the second node 16B of the second planetarygear set 16 and third node 18C of the third planetary gear set 18 withthe stationary element or a transmission housing 50. A fourth brake 34selectively connects the first node 18A of the third planetary gear set18 with the stationary element or a transmission housing 50.

Referring now to FIG. 2, a stick diagram presents a schematic layout ofthe embodiment of the ten speed transmission 10 according to the presentinvention. In FIG. 2, the numbering from the lever diagram of FIG. 1 iscarried over. The clutches, brakes, and couplings are correspondinglypresented whereas the nodes of the planetary gear sets now appear ascomponents of planetary gear sets such as sun gears, ring gears, planetgears and planet gear carriers.

In an embodiment of the present invention, planetary gear set 14includes a sun gear member 14C, a ring gear member 14A and a planet gearcarrier member 14B that rotatably supports a set of planet gears 14D(only one of which is shown). The planet gears 14D are each configuredto intermesh with both the sun gear member 14C and ring gear member 14A.The sun gear member 14C is connected for common rotation with a firstshaft or interconnecting member 42 and with input member 12. The planetcarrier member 14B is connected for common rotation with a second shaftor interconnecting member 44 and a third shaft or interconnecting member46. The ring gear member 14A is connected for common rotation with afourth shaft or interconnecting member 48.

The planetary gear set 16 includes a sun gear member 16A, a ring gearmember 16C and a planet gear carrier member 16B that rotatably supportsa set of planet gears 16D (only one of which is shown). The planet gears16D are each configured to intermesh with both the sun gear member 16Aand the ring gear member 16C. The sun gear member 16A is connected forcommon rotation with a fifth shaft or interconnecting member 52. Thering gear member 16C is connected for common rotation with a sixth shaftor interconnecting member 54. The planet carrier member 16B is connectedfor common rotation with the fourth shaft or interconnecting member 48and a seventh shaft or interconnecting member 56.

In an embodiment of the present invention, planetary gear sets 18 and 20(shown in the lever diagram of FIG. 1) are combined to form a planetarygear set assembly 19. Planetary gear set assembly 19 includes a firstsun gear member 18C, a second sun gear member 20C, a first ring gearmember 18A, a second ring gear member 20A and a planet gear carriermember 18B/20B that rotatably supports a first set of planet gears 18D(only one of which is shown) and a second set of planet gears 20D (onlyone of which is shown). The first set of planet gears 18D are eachconfigured to intermesh with both the first sun gear member 18C and thefirst ring gear member 18A. The second set of planet gears 20D are eachconfigured to intermesh with both the second sun gear member 20C at afirst end 20E and the second ring gear member 20A at a second end 20F.The first ring gear member 18A is connected for common rotation with aneighth shaft or interconnecting member 58. The first sun gear member 18Cis connected for common rotation with the seventh shaft orinterconnecting member 56. The second sun gear member 20C is connectedfor common rotation with the fifth shaft or interconnecting member 52.The second ring gear member 20A is connected for common rotation withthe output shaft 22. The planet carrier member 18B/20B is connected forcommon rotation with the ninth shaft or interconnecting member 60.

The input shaft or member 12 is continuously connected to an engine (notshown) or to a turbine of a torque converter (not shown). The outputshaft or member 22 is continuously connected with the final drive unitor transfer case (not shown).

The torque-transmitting mechanisms or first clutch 24, second clutch 26,first brake 28, second brake 30, third brake 32 and fourth brake 34allow for selective interconnection of the shafts or interconnectingmembers, members of the planetary gear sets and the housing. Forexample, the first clutch 24 is selectively engageable to connect theinput shaft member 12 and the first shaft or interconnecting member 42with the ninth shaft or interconnecting member 60. The second clutch 26is selectively engageable to connect the third shaft or interconnectingmember 46 and the sixth shaft or interconnecting member 54 with theninth shaft or interconnecting member 60. The first brake 28 isselectively engageable to connect the second shaft or interconnectingmember 44 with the stationary element or the transmission housing 50 inorder to prevent the member 44 from rotating relative to thetransmission housing 50. The second brake 30 is selectively engageableto connect the fifth shaft or interconnecting member 52 with thestationary element or the transmission housing 50 in order to preventthe member 52 from rotating relative to the transmission housing 50. Thethird brake 32 is selectively engageable to connect the fourth shaft orinterconnecting member 48 with the stationary element or thetransmission housing 50 in order to prevent the member 48 from rotatingrelative to the transmission housing 50. The fourth brake 34 isselectively engageable to connect the eighth shaft or interconnectingmember 58 with the stationary element or the transmission housing 50 inorder to prevent member 58 from rotating relative to the transmissionhousing 50.

Referring now to FIGS. 2 and 3, the operation of the embodiment of theten speed transmission 10 will be described. It will be appreciated thatthe transmission 10 is capable of transmitting torque from the inputshaft or member 12 to the output shaft or member 22 in at least tenforward speed or torque ratios and at least one reverse speed or torqueratio with triple overdrive. Each forward and reverse speed or torqueratio is attained by engagement of one or more of thetorque-transmitting mechanisms (i.e. first clutch 24, second clutch 26,first brake 28, second brake 30, third brake 32 and fourth brake 34), aswill be explained below. FIG. 3 is a truth table presenting the variouscombinations of torque-transmitting elements that are activated orengaged to achieve the various gear states. Actual numerical gear ratiosof the various gear states are also presented although it should beappreciated that these numerical values are exemplary only and that theymay be adjusted over significant ranges to accommodate variousapplications and operational criteria of the transmission 10. An exampleof the gear ratios that may be obtained using the embodiments of thepresent invention are also shown in FIG. 3. Of course, other gear ratiosare achievable depending on the gear diameter, gear teeth count and gearconfiguration selected.

To establish reverse gear, the first clutch 24 and the fourth brake 34are engaged or activated. The first clutch 24 selectively interconnectsthe input shaft member 12 and the first shaft or interconnecting member42 with the ninth shaft or interconnecting member 60. The fourth brake34 connects the eighth shaft or interconnecting member 58 with thestationary element or the transmission housing 50 in order to preventmember 58 from rotating relative to the transmission housing 50.Likewise, the ten forward ratios are achieved through differentcombinations of clutch and brake engagement, as shown in FIG. 3.

Referring now to FIGS. 2 and 4, the operation of an alternate embodimentof the transmission 10 that is capable of establishing ten or elevenspeeds will be described. It will be appreciated that the transmission10 is capable of transmitting torque from the input shaft or member 12to the output shaft or member 22 in at least eleven forward speed ortorque ratios and at least one reverse speed or torque ratio with tripleoverdrive. Each forward and reverse speed or torque ratio is attained byengagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 24, second clutch 26, first brake 28, second brake 30,third brake 32 and fourth brake 34), as will be explained below. FIG. 4is a truth table presenting the various combinations oftorque-transmitting elements that are activated or engaged to achievethe various gear states. Actual numerical gear ratios of the variousgear states are also presented although it should be appreciated thatthese numerical values are exemplary only and that they may be adjustedover significant ranges to accommodate various applications andoperational criteria of the transmission 10. An example of the gearratios that may be obtained using the embodiments of the presentinvention are also shown in FIG. 4. Of course, other gear ratios areachievable depending on the gear diameter, gear teeth count and gearconfiguration selected.

To establish the eleventh gear ratio, the first clutch 24 and the firstbrake 28 are engaged or activated. The first clutch 24 selectivelyinterconnects the input shaft member 12 and the first shaft orinterconnecting member 42 with the ninth shaft or interconnecting member60. The first brake 28 connects the second shaft or interconnectingmember 44 with the stationary element or the transmission housing 50 inorder to prevent the member 44 from rotating relative to thetransmission housing 50. Likewise, the other ten forward ratios andreverse ratio are achieved through different combinations of clutch andbrake engagement, as shown in FIG. 4.

It will be appreciated that the foregoing explanation of operation andgear states of the transmission 10 assumes, first of all, that all theclutches and brakes not specifically referenced in a given gear stateare inactive or disengaged and, second of all, that during gear shifts,i.e., changes of gear state, between at least adjacent gear states, aclutch or brake engaged or activated in both gear states will remainengaged or activated.

The description of the invention is merely exemplary in nature andvariations that do not depart from the gist of the invention areintended to be within the scope of the invention. Such variations arenot to be regarded as a departure from the spirit and scope of theinvention.

1. A transmission comprising: an input member; an output member; a firstplanetary gear set having a first, a second and a third member andwherein the input member is continuously interconnected with the thirdmember of the first planetary gear set; a second planetary gear sethaving a first, a second and a third member; a planetary gear setassembly having a first member, a second member, a third member, afourth member and a fifth member and wherein the output member iscontinuously interconnected with the fifth member of the planetary gearset assembly; a first interconnecting member continuouslyinterconnecting the first member of the first planetary gear set withthe second member of the second planetary gear set and the third memberof the planetary gear set assembly; a second interconnecting membercontinuously interconnecting the second member of the first planetarygear set with the third member of the second planetary gear set; a thirdinterconnecting member continuously interconnecting the first member ofthe second planetary gear set with the fourth member of the planetarygear set assembly; and at least six torque transmitting mechanisms eachselectively engageable to interconnect at least one of the first,second, third, fourth and fifth members of the planetary gear setassembly or at least one of the first, second and third members of thefirst and second planetary gear sets; with at least one of another ofthe first, second, third, fourth and fifth members of the planetary gearset assembly, another of the first, second and third members of thefirst and second planetary gear sets, or a stationary member; andwherein the at least six torque transmitting mechanisms are eachselectively engageable in combinations of at least two to establish atleast ten forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.
 2. The transmission ofclaim 1 wherein a first of the six torque transmitting devices isselectively engageable to interconnect the input shaft member and thethird member of the first planetary gear set with the second member ofthe planetary gear set assembly.
 3. The transmission of claim 2 whereina second of the six torque transmitting devices is selectivelyengageable to interconnect the second member of the first planetary gearset and the third member of the second planetary gear set with thesecond member of the planetary gear set assembly.
 4. The transmission ofclaim 3 wherein a third of the six torque transmitting devices isselectively engageable to interconnect the second member of the firstplanetary gear set with the stationary member.
 5. The transmission ofclaim 4 wherein a fourth of the six torque transmitting devices isselectively engageable to interconnect the first member of the secondplanetary gear set and the fourth member of the planetary gear setassembly with the stationary member.
 6. The transmission of claim 5wherein a fifth of the six torque transmitting devices is selectivelyengageable to interconnect the first member of the first planetary gearset, the second member of the second planetary gear set and the thirdmember of the planetary gear set assembly with the stationary member. 7.The transmission of claim 6 wherein a sixth of the six torquetransmitting devices is selectively engageable to interconnect the firstmember of the planetary gear set assembly with the stationary member. 8.The transmission of claim 1 wherein the third member of the firstplanetary gear set, the first member of the second planetary gear set,and the third and fourth members of the planetary gear set assembly aresun gears, the second member of the first and second planetary gear setsand the second member of the planetary gear set assembly are carriermembers, and the first member of the first planetary gear set, the thirdmember of the second planetary gear set and the first and fifth membersof the planetary gear set assembly are ring gears.
 9. The transmissionof claim 1 wherein two of the six torque transmitting devices areclutches and four of the six torque transmitting devices are brakes. 10.The transmission of claim 1 wherein the stationary member is atransmission housing.
 11. A transmission comprising: an input member; anoutput member; a first planetary gear set having a first, a second and athird member, wherein the input member is continuously interconnectedwith the third member of the first planetary gear set; a secondplanetary gear set having a first, a second and a third member; aplanetary gear set assembly having a first member, a second member, athird member, a fourth member and a fifth member, wherein the outputmember is continuously interconnected with the fifth member of theplanetary gear set assembly; a first interconnecting member continuouslyinterconnecting the first member of the first planetary gear set withthe second member of the second planetary gear set and the third memberof the planetary gear set assembly; a second interconnecting membercontinuously interconnecting the second member of the first planetarygear set with the third member of the second planetary gear set; a thirdinterconnecting member continuously interconnecting the first member ofthe second planetary gear set with the fourth member of the planetarygear set assembly; a first torque transmitting device selectivelyengageable to interconnect the input member and the third member of thefirst planetary gear set with the second member of the planetary gearset assembly; a second torque transmitting device selectively engageableto interconnect the second member of the first planetary gear set andthe third member of the second planetary gear set with the second memberof the planetary gear set assembly; a third torque transmitting deviceselectively engageable to interconnect the second member of the firstplanetary gear set with the stationary member; a fourth torquetransmitting device selectively engageable to interconnect the firstmember of the second planetary gear set and the fourth member of theplanetary gear set assembly the with the stationary member; a fifthtorque transmitting device selectively engageable to interconnect thefirst member of the first planetary gear set, the second member of thesecond planetary gear set and the third member of the planetary gear setassembly with the stationary member; and a sixth torque transmittingdevice selectively engageable to interconnect the first member of theplanetary gear set assembly with the stationary member, and wherein thetorque transmitting devices are each selectively engageable incombinations of at least two to establish at least ten forward speedratios and at least one reverse speed ratio between the input member andthe output member.
 12. The transmission of claim 11 wherein the thirdmember of the first planetary gear set, the first member of the secondplanetary gear set, and the third and fourth members of the planetarygear set assembly are sun gears, the second member of the first andsecond planetary gear sets and the second member of the planetary gearset assembly are carrier members, and the first member of the firstplanetary gear set, third member of the second planetary gear set andthe first and fifth members of the planetary gear set assembly are ringgears.
 13. The transmission of claim 11 wherein the stationary member isa transmission housing.
 14. A transmission comprising: an input member;an output member; a first planetary gear set having a sun gear, acarrier member and a ring gear, wherein the input member is continuouslyinterconnected with the sun gear of the first planetary gear set; asecond planetary gear set having a sun gear, a carrier member and a ringgear; a planetary gear set assembly having a first sun gear, a secondsun gear, a first ring gear, a second ring gear and a carrier member,wherein the output member is continuously interconnected with the secondring gear of the planetary gear set assembly; a first interconnectingmember continuously interconnecting the ring gear of the first planetarygear set with the carrier member of the second planetary gear set andthe first sun gear of the planetary gear set assembly; a secondinterconnecting member continuously interconnecting the carrier memberof the first planetary gear set with the ring gear member of the secondplanetary gear set; a third interconnecting member continuouslyinterconnecting the sun gear of the second planetary gear set with thesecond sun gear of the planetary gear set assembly; a first torquetransmitting device selectively engageable to interconnect the inputmember and the sun gear of the first planetary gear set with the carriermember of the planetary gear set assembly; a second torque transmittingdevice selectively engageable to interconnect the carrier member of thefirst planetary gear set and the ring gear of the second planetary gearset with the carrier member of the planetary gear set assembly; a thirdtorque transmitting device selectively engageable to interconnect thecarrier member of the first planetary gear set with the stationarymember; a fourth torque transmitting device selectively engageable tointerconnect the sun gear of the second planetary gear set and thesecond sun gear of the planetary gear set assembly the with thestationary member; a fifth torque transmitting device selectivelyengageable to interconnect the ring gear of the first planetary gearset, the carrier member of the second planetary gear set and the firstsun gear of the planetary gear set assembly with the stationary member;and a sixth torque transmitting device selectively engageable tointerconnect the first ring gear of the planetary gear set assembly withthe stationary member, and wherein the torque transmitting devices areeach selectively engageable in combinations of at least two to establishat least ten forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.
 15. The transmission ofclaim 14 wherein the stationary member is a transmission housing.